EP2180207B1 - Support antivibratoire hydraulique et véhicule comportant un tel support - Google Patents

Support antivibratoire hydraulique et véhicule comportant un tel support Download PDF

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Publication number
EP2180207B1
EP2180207B1 EP09172474A EP09172474A EP2180207B1 EP 2180207 B1 EP2180207 B1 EP 2180207B1 EP 09172474 A EP09172474 A EP 09172474A EP 09172474 A EP09172474 A EP 09172474A EP 2180207 B1 EP2180207 B1 EP 2180207B1
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EP
European Patent Office
Prior art keywords
plate
chamber
flexible membrane
antivibration support
une
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP09172474A
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German (de)
English (en)
French (fr)
Other versions
EP2180207A1 (fr
Inventor
Gabriel Lemaire
Pascal Petit
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hutchinson SA
Original Assignee
Hutchinson SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hutchinson SA filed Critical Hutchinson SA
Priority to PL09172474T priority Critical patent/PL2180207T3/pl
Publication of EP2180207A1 publication Critical patent/EP2180207A1/fr
Application granted granted Critical
Publication of EP2180207B1 publication Critical patent/EP2180207B1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K5/00—Arrangement or mounting of internal-combustion or jet-propulsion units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
    • F16F13/105—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like characterised by features of partitions between two working chambers
    • F16F13/106—Design of constituent elastomeric parts, e.g. decoupling valve elements, or of immediate abutments therefor, e.g. cages
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K5/00—Arrangement or mounting of internal-combustion or jet-propulsion units
    • B60K5/12—Arrangement of engine supports

Definitions

  • the present invention relates to hydraulic antivibration mounts and vehicles comprising such supports.
  • WO / 2004/081408 describes an example of such a hydraulic support, in which a piston moves in the intermediate chamber and which opens or closes an extension of the first constricted passage towards the compensation chamber as a function of the amplitudes of the vibrations to which the vibratory support is subjected, the piston being returned to its rest position by a spring.
  • the present invention is intended to provide an antivibration support which has an improvement in removing the disadvantages of the prior art.
  • an antivibration support of the kind in question is defined by the features of claim 1.
  • the invention also relates to a vehicle comprising a body and a motor connected to the body by at least one antivibration support as defined above.
  • the figure 1 represents a motor vehicle V whose body CV supports a motor M by means of at least one hydraulic antivibration support 1 such as that shown on the figures 2 , 3 and 4 in one embodiment of the invention.
  • the second rigid reinforcement 9 can be covered as in the example shown in the figures, by a layer of elastomeric material integral with the elastomer body 14, both on its outer portion 96 and on its inner portion 95.
  • the elastomer body 14 delimits with this first plate 2 a working chamber A filled with liquid, the operation of which will be described in detail below.
  • a non-return valve 8 made of flexible material, comprising a disc 81 pressed against the flat plate 22 and sealingly covering the inlet orifices 20 in the resting state, and an outgrowth axial axis Z1, mushroom-shaped 82, received in the central orifice 21.
  • the head of this mushroom 82 has a diameter greater than the central orifice 21, and the stem of this mushroom 82 has a diameter substantially equal to the central orifice 21, and taking into account the possibilities of deformation of the flexible material of the mushroom, it can be inserted the central orifice 21, and is held and locked in its position (as shown in the figures) once inserted .
  • the disk 81 is flexible, it can be deformed under the effect of the liquid pressure at the inlet ports 20 to let liquid, as will be described later in detail.
  • the nonreturn valve 8 may optionally be equipped with a reinforcing core (not shown in the figures) housed in its disk 81 and / or in the protuberance 82 in the form of a mushroom.
  • a rigid flange 30 is inserted without clearance between the first and second plates 2,4 described above, the rigid flange 30 being integral with the second frame 9.
  • This rigid flange 30 has a generally annular shape, comprises a circumferential flat portion located at the outer periphery, perpendicular to the axis Z1, and an inner edge bent in the axial direction.
  • the circumferential flat portion of this flange is pierced by a leakage hole 33 of small size which is found opposite the calibrated hole 46, is also pierced by a transfer orifice 31 in the form of a bean situated opposite of the cavity 44, and has a notch 32 on its circumference in which the protuberance 43 is received.
  • a flexible membrane 3 of elastomer On this rigid flange 30 is attached a flexible membrane 3 of elastomer, symmetrical of revolution about the axis Z1, its peripheral portion being overmolded on the inner curved edge of the rigid flange 30.
  • the flexible membrane 3 comprises a peripheral zone 36 adjacent to the curved inner edge of the flange, a bulge 37 projecting axially upwards, a movable wall 38 able to move axially, a reinforcing insert 35 in the form of a flat disk housed in the central portion of the movable wall 38 and of diameter slightly greater than the diameter of the main orifice 41.
  • the flexible membrane 3 is shown in FIG. figure 4 in solid line in its rest position, and in mixed line in its activated position, in which it closes the main orifice, 41 said membrane being able to deform under the effect of pressure differences between its two faces.
  • the flexible membrane 3 delimits with the second plate 4 an intermediate chamber B, filled with liquid, and in addition the flexible membrane 3 delimits with the first plate 2 an auxiliary chamber D, filled with liquid, the hydraulic operation of these intermediate and auxiliary chambers will be described later.
  • a stud 10 or any other fastening means is received in the central hole 64, to attach the hydraulic antivibration support 1 to the CV body of the vehicle.
  • an anti-return valve 8 makes it possible to feed the auxiliary chamber D, under certain vibratory stress conditions, by means of a first flow path 18, shown in FIG. figure 6 .
  • the antivibration support which has just been described operates as follows.
  • the vibrations of the motor M When the vehicle engine is running at low speed, the vibrations of the motor M, with a frequency generally of between 15 and 200 Hz (in particular preferably between 15 and 50 Hz) and of amplitude generally less than 0.1 or 0.2 mm , are transmitted to the working chamber A by the elastomer body 14, which causes fluctuations in the volume of said working chamber A which are transmitted by the first throttled passage 11 to the intermediate chamber B, which is in fluid communication with low resistance with the compensation chamber C through the main orifice 41.
  • the resonant frequency of the first throttled passage 11 substantially corresponds to the frequency of the vibrations emitted by the engine at idle, said first throttled passage 11 is then the seat of resonance that effectively dampen the vibrations of the engine.
  • the second throttled passage 12 is inactive or "short-circuited" because the fluid passes through the main orifice 41 which has a much greater ease of passage than that of the second throttled passage 12.
  • the non-return valve 8 does not fulfill a significant decoupling function that would absorb vibrations of relatively high frequency (for example of the order of 15 to 200 Hz) and relatively low amplitude (for example less than about 0 , 1 or 0.2 mm).
  • the non-return valve 8 may optionally open and close alternately, and each time it opens, a quantity of liquid is transferred from the working chamber A to the auxiliary chamber D, which tends to increase the pressure in the auxiliary chamber D.
  • the leakage passage 46 passes, with a certain flow rate, fluid from the auxiliary chamber D to the compensation chamber C along the second path flow 19 which has been described above, which causes the opposite effect, that is to say the tendency to reduce the pressure in the auxiliary chamber D.
  • the rolling causes vibratory movements of large amplitude (for example, greater than 0.1 or 0.2 mm) and low frequency (less than 20 Hz) of the motor M with respect to the body CV, and these greater vibratory movements cause the alternative forced opening of the non-return valve 8, which causes the filling of the auxiliary chamber D with a flow rate greater than the flow rate authorized by the leakage passage 46 in the second flow path 19, which has the effect of increasing the pressure in the auxiliary chamber D, and pushing the flexible membrane 3 towards the main orifice 41.
  • large amplitude for example, greater than 0.1 or 0.2 mm
  • low frequency less than 20 Hz
  • the auxiliary chamber fills up faster than it empties and the flexible membrane 3 comes to match the shape of the bowl portion formed in the second plate 4, so that the movable wall 38 of the flexible membrane 3 is pressed against the bottom of the bowl and in particular causes the obstruction of the main orifice 41, which configuration is shown in FIG. figure 6 .
  • the reinforcing insert 35 is pressed against the main orifice 41, and as the diameter of the reinforcing insert 35 is greater than that of the main orifice 41, any intrusion of the flexible membrane 3 inside the main orifice 41 or even the compensation chamber C is avoided.
  • the only fluid communication channel between the intermediate chamber B and the compensation chamber C is the second throttled passage 12, which has a lower ease of passage than the first constricted passage 11, to which it is connected in 'series' mode.
  • the fluid displacements between the working chamber A and the compensation chamber C are along a path that includes the first throttled passage 11, the intermediate chamber B and the second throttled passage 12, the damping characteristics of the second throttled passage 12 being preponderant, and therefore the resonant frequency is less than 20 Hz and a fluttering effect in this frequency zone can properly dampen the movements related to rolling, also called 'mince' movements.
  • the valve 8 When the vibratory movements of large amplitude cease, the valve 8 remains closed and the auxiliary chamber D empties through the leakage passage 46 along the second flow path 19, the flexible membrane 3 then returns elastically to its rest position, by its own elastic characteristics, by releasing the passage of liquid through the main orifice 41, and 'short-circuiting' the second throttled passage 12, which amounts to recovering the damping characteristics of the 'idle' mode, described above.
  • first constricted passage 11 ' which connects the working chamber A to the intermediate chamber B, are identical or similar to those described in the first embodiment and therefore will not be described again in detail. right here.
  • the first plate 2 'therefore differs from the first plate 2 of the first embodiment in that it comprises the first section 120 of the second constricted passage 12' and that the groove 11 'of the first passage choke is shifted radially towards the center.
  • the second plate 4 ' differs from the second plate 4 of the first embodiment in that it comprises the second section 124 of the second throttled passage 12' (instead of the whole of the second throttled passage 12).
  • the antivibration support according to this second embodiment operates, mutatis mutandis, as follows.
  • the vibrations of the motor M are transmitted to the working chamber A by the elastomer body 14, which causes volume fluctuations of said working chamber A which are transmitted by the first constricted passage 11 'to the intermediate chamber B, which is in low resistance fluid communication with the compensation chamber C through the main orifice 41.
  • the resonant frequency of the first throttled passage 11 ' substantially corresponds to the frequency of the vibrations emitted by the engine at idle, said first throttled passage 11' is then the seat of resonance phenomena that effectively dampen the vibrations of the engine.
  • the second throttled passage 12 ' is inactive or' short-circuited 'because the fluid passes through the first throttled passage 11' and the main orifice 41, a path which has a much greater ease of passage.
  • the non-return valve 8 can open and close alternately, and let a quantity of liquid flow from the working chamber A to the auxiliary chamber D, but, as has been described for the first embodiment, the flow of the leakage passage 46 is greater so that the flexible membrane 3 deviates little from its rest position.
  • the rolling causes vibratory movements of large amplitude (for example, greater than 0.1 or 0.2 mm) and low frequency (less than 20 Hz) of the motor M with respect to the body CV, which have the effect as described for the first embodiment, to cause the inflation of the auxiliary chamber D and the closure of the main orifice 41.
  • large amplitude for example, greater than 0.1 or 0.2 mm
  • low frequency less than 20 Hz
  • the characteristics of the second constricted passage 12 'whose resonant frequency is less than 20 Hz make it possible, by a fluid beating effect in this frequency zone, to dampen properly the motions related to rolling, also known as' hash movements'. .
  • the valve 8 When the vibratory movements of large amplitude cease, the valve 8 remains closed and the auxiliary chamber D empties through the leakage passage 46 along the second flow path 19, the flexible membrane 3 then returns elastically to its rest position, by its own elastic characteristics, by releasing the passage of liquid through the main orifice 41, which restores the communication between the first constricted passage 11 'and the compensation chamber C via the main orifice 41.
  • the flexible membrane 3 When the flexible membrane 3 returns to its rest position, it no longer closes the main orifice 41 and the auxiliary chamber D then communicates with the compensation chamber C via the intermediate chamber B and the main orifice 41, again according to the flow path 190.
  • the thickened edges 84a and 84b may have for example a thickness of the order of 4 to 5 mm.
  • the valve 8 ' is disposed under the first plate 2 and more particularly in correspondence with the orifices 20 of this plate, and it is held under the first plate 2 by the rigid holding grid 83, made for example of thermoplastic material and extending in a general plane perpendicular to the axis Z1.
  • the holding grid 83 is fixed to the first plate 2 and the flexible elastomer membrane 84 is interposed between the first plate 2 and said holding grid 83.
  • Said holding grid 83 comprises a central portion 74 in the form of a disc centered on the axis Z1.
  • Said central portion 74 is provided with tabs 76, for example four in number, which each extend substantially parallel to the axis Z1 to a free end provided with a hook 86 oriented radially outwardly.
  • tabs 76 are received in the orifice 21 of the first plate 2 already described, and the hooks 86 are clipped on top of said plate 2 to ensure the fixing of the holding grid 83 on the first plate 2.
  • the holding grid 83 further comprises spokes 88 extending from the central portion 74, radially outwardly to a rim 75 of circular shape. From this rim 75 extend, radially outwardly, peripheral portions 87 which are here four in number and are here equidistributed angularly around the axis Z1. These peripheral portions 87 each comprise a radial portion 87a perpendicular to the axis Z1 and a cylinder portion 87b centered on the axis Z1, directed towards the first plate 2 and intended to remain in contact with the flat plate 22 of the first plate .
  • the four peripheral portions 87 are evenly spaced around the periphery of the rim 75, and between these four peripheral peripheral portions 87 are formed four intervals 87c, each extending over approximately 45 °.
  • the radial portions 87a of the different peripheral portions 87 form, with the spokes 88, an upper flat surface perpendicular to the axis Z1, oriented towards the elastomer membrane 84.
  • the cylinder portions 87b of the peripheral portions 87 and the central portion 74 of the holding grid 83 projects towards the plate 2 of the same height from this flat upper surface, so that the upper edges of the cylinder parts 87b and of the central part 74 bear against the flat lower surface of the first platinum 2.
  • the thickened inner edge 84a of the flexible elastomeric membrane 84 is substantially of the same diameter as the central portion 74 of the holding grid 83, and said thickened inner edge is fitted without play around the central portion.
  • the thickened outer edge 84b of said membrane is fitted inside the cylindrical portions 87b.
  • the thickened inner edge 84a is in contact both against the spokes 88 and the lower surface of the first plate 2
  • the thickened outer edge 84b is in contact both against the upper surface of the radial portions 87a of the portions. 87 and against the lower surface of the first plate 2.
  • the thickened outer edge 84b of the elastomer membrane 84 is not supported downwardly (i.e. towards chamber D) at the four intervals 87c, which gives it the possibility of deforming under the pressure of fluid coming from the A.
  • This deformation is represented in dashed line on the figure 10 , on the left side, with the mark 99.
  • the flexible elastomer membrane 84 acts as a decoupling membrane and deforms slightly without its edge 89 coming off the lower face 25 of the first plate 2. In this case, there is no filling of the auxiliary chamber D and the flexible elastomer membrane 84 alone absorbs the vibrations, thus preventing them from being transmitted to the vehicle body.
  • the flexible membrane 3 does not close the main orifice 41, so that the flexible elastomer membrane 84 can vibrate freely by absorbing the vibrations of the motor, the small volume variations corresponding to these vibrations being themselves same absorbed by deformations of the flexible bag 5.
  • the operation of the filling and purging of the auxiliary chamber D is similar to that described for the first three embodiments.
  • the closure of the main port 41 and the switching from one operating mode to the other and vice versa is also similar to that described for the first three embodiments.
  • the elements of the non-return valve 8 'described in the fourth mode can of course be associated with the elements of the second and / or third embodiment described above.
  • first and second armatures 7, 9 can be easily adapted to suit different mountings on the CV box or the motor M.
  • the second armature 9 can have an external shoulder at any level of its periphery. outside to be received in a corresponding housing belonging to the body CV of the vehicle.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
  • Blow-Moulding Or Thermoforming Of Plastics Or The Like (AREA)
  • Springs (AREA)
EP09172474A 2008-10-23 2009-10-07 Support antivibratoire hydraulique et véhicule comportant un tel support Active EP2180207B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL09172474T PL2180207T3 (pl) 2008-10-23 2009-10-07 Hydrauliczna podpora przeciwwstrząsowa oraz pojazd wyposażony w taką podporę przeciwwstrząsową

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0857216A FR2937702B1 (fr) 2008-10-23 2008-10-23 Support antivibratoire hydraulique et vehicule comportant un tel support

Publications (2)

Publication Number Publication Date
EP2180207A1 EP2180207A1 (fr) 2010-04-28
EP2180207B1 true EP2180207B1 (fr) 2011-09-28

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ID=40577922

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09172474A Active EP2180207B1 (fr) 2008-10-23 2009-10-07 Support antivibratoire hydraulique et véhicule comportant un tel support

Country Status (9)

Country Link
US (1) US8240644B2 (ja)
EP (1) EP2180207B1 (ja)
JP (1) JP5514508B2 (ja)
KR (1) KR101622401B1 (ja)
CN (1) CN101725661B (ja)
AT (1) ATE526514T1 (ja)
BR (1) BRPI0904203A2 (ja)
FR (1) FR2937702B1 (ja)
PL (1) PL2180207T3 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017103603A1 (de) 2017-02-22 2018-08-23 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Hydrolager zur Lagerung eines Aggregats eines Kraftfahrzeugs

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CN102913588B (zh) * 2011-08-02 2015-03-25 上海汽车集团股份有限公司 一种半主动悬置
JP5909077B2 (ja) * 2011-11-08 2016-04-26 東洋ゴム工業株式会社 防振ユニット
JP6251175B2 (ja) * 2012-09-10 2017-12-20 株式会社フコク 液体封入式マウント
DE102012217427A1 (de) * 2012-09-26 2014-05-28 Bayerische Motoren Werke Aktiengesellschaft Hydrolager, insbesondere Aggregatlager für ein Kraftfahrzeug
CN103758917B (zh) * 2013-12-30 2016-02-03 长城汽车股份有限公司 发动机液压悬置及具有该发动机液压悬置的车辆
FR3017673B1 (fr) * 2014-02-14 2016-02-12 Hutchinson Support antivibratoire hydraulique pilotable
JP6423891B2 (ja) * 2014-03-12 2018-11-14 ユチンソンＨｕｔｃｈｉｎｓｏｎ 発電機が設けられた油圧振動抑制装置
DE102014118502B4 (de) 2014-12-12 2018-09-06 Vibracoustic Gmbh Lageranordnung zum Lagern eines Motors
US10145443B2 (en) 2015-01-26 2018-12-04 Itt Manufacturing Enterprises Llc Compliant elastomeric shock absorbing apparatus
DE102016110703A1 (de) * 2016-06-10 2017-12-14 Vibracoustic Gmbh Hydrolager
CN108131415A (zh) * 2016-12-01 2018-06-08 江苏骆氏减震件有限公司 解耦膜片及包括其的液阻悬置
US10544851B2 (en) * 2017-02-23 2020-01-28 Ford Global Technologies, Llc Vehicular vibration isolation system and apparatus
DE102018102130A1 (de) * 2018-01-31 2019-08-01 Vibracoustic Gmbh Hydraulisch dämpfendes Lager
FR3079578B1 (fr) * 2018-04-03 2021-02-19 Hutchinson Dispositif antivibratoire et vehicule comportant un tel dispositif antivibratoire
CN112576681B (zh) * 2019-09-27 2023-02-24 现代自动车株式会社 用于车辆的悬置
CN113494557B (zh) * 2021-07-27 2022-07-05 重庆长安汽车股份有限公司 一种解耦膜、悬置总成及车辆

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JP3608035B2 (ja) * 1999-09-10 2005-01-05 東洋ゴム工業株式会社 切替制御型の液封入式防振装置
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CN100543338C (zh) * 2005-09-14 2009-09-23 东海橡胶工业株式会社 流体填充式减振装置
US20070090579A1 (en) * 2005-10-21 2007-04-26 Paulstra Crc Hydraulic antivibration device
JP4861969B2 (ja) * 2007-11-30 2012-01-25 東海ゴム工業株式会社 流体封入式防振装置
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JP5081688B2 (ja) * 2008-03-28 2012-11-28 株式会社ブリヂストン 防振装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017103603A1 (de) 2017-02-22 2018-08-23 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Hydrolager zur Lagerung eines Aggregats eines Kraftfahrzeugs
WO2018153794A1 (de) 2017-02-22 2018-08-30 Vibracoustic Gmbh Hydrolager zur lagerung eines aggregats eines kraftfahrzeugs
US11215262B2 (en) 2017-02-22 2022-01-04 Vibracoustic Se Hydraulic bearing for supporting an assembly of a motor vehicle
DE102017103603B4 (de) 2017-02-22 2023-03-16 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Hydrolager zur Lagerung eines Aggregats eines Kraftfahrzeugs

Also Published As

Publication number Publication date
BRPI0904203A2 (pt) 2011-02-01
PL2180207T3 (pl) 2012-07-31
EP2180207A1 (fr) 2010-04-28
FR2937702B1 (fr) 2010-11-26
US8240644B2 (en) 2012-08-14
JP2010101494A (ja) 2010-05-06
US20100109218A1 (en) 2010-05-06
ATE526514T1 (de) 2011-10-15
CN101725661B (zh) 2013-06-19
JP5514508B2 (ja) 2014-06-04
FR2937702A1 (fr) 2010-04-30
KR101622401B1 (ko) 2016-05-18
CN101725661A (zh) 2010-06-09
KR20100045395A (ko) 2010-05-03

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